U.S. patent number 8,851,112 [Application Number 13/466,939] was granted by the patent office on 2014-10-07 for dual configuration hydraulic manifold apparatus and system.
This patent grant is currently assigned to 1566618 Alberta Ltd.. The grantee listed for this patent is Travis Nelson. Invention is credited to Travis Nelson.
United States Patent |
8,851,112 |
Nelson |
October 7, 2014 |
Dual configuration hydraulic manifold apparatus and system
Abstract
The invention relates to a hydraulic manifold apparatus and
system, connectable to a dual stage motor, for use in the topdrive
of drilling operations. The hydraulic manifold is switchable
between a low speed, high torque configuration and a high speed,
low torque configuration. Valves within the manifold control the
flow of working fluid through the manifold and into and out of the
motor. Switching means are further provided to control the opening
and closing of the valves. In the low speed, high torque
configuration, working fluid enters each stage of the dual motor
simultaneously, in parallel. In the high speed, low torque
configuration, working fluid enters a first stage of the motor,
returns to the hydraulic manifold, then enters a second stage of
the motor, before returning again to the hydraulic manifold. Thus
during high speed, low torque operation, working fluid enters each
stage of the dual motor in series.
Inventors: |
Nelson; Travis (Calgary,
CA) |
Applicant: |
Name |
City |
State |
Country |
Type |
Nelson; Travis |
Calgary |
N/A |
CA |
|
|
Assignee: |
1566618 Alberta Ltd. (Calgary,
CA)
|
Family
ID: |
49547697 |
Appl.
No.: |
13/466,939 |
Filed: |
May 8, 2012 |
Prior Publication Data
|
|
|
|
Document
Identifier |
Publication Date |
|
US 20130299020 A1 |
Nov 14, 2013 |
|
Current U.S.
Class: |
137/596.17;
91/519; 91/508; 137/625.65; 91/520; 137/565.11 |
Current CPC
Class: |
F04B
53/1082 (20130101); F04B 49/22 (20130101); Y10T
137/86622 (20150401); Y10T 137/87217 (20150401); Y10T
137/85986 (20150401) |
Current International
Class: |
F16K
31/02 (20060101) |
Field of
Search: |
;137/596.17,625.65,565.11 ;91/508,519,520,522-523 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Houston; Elizabeth
Assistant Examiner: Le; Minh
Attorney, Agent or Firm: Bennett Jones LLP
Claims
I claim:
1. A hydraulic manifold apparatus operable in a low speed, high
torque configuration or a high speed, low torque configuration,
said hydraulic manifold apparatus comprising: a supply port adapted
to receive pressurized working fluid from a hydraulic pump; a first
and second output port connectable to an intake of a hydraulic
motor; a first and second intake port connectable to an output of
said hydraulic motor; a first, second, and third actuable valve for
controlling the flow of said working fluid through said hydraulic
manifold apparatus; actuation means including a first solenoid, a
second solenoid, and a third solenoid for actuating said first
actuable valve, said second actuable valve, and said third actuable
valve, respectively, in said hydraulic manifold apparatus between a
first configuration for low speed, high torque operation wherein
said first actuable valve and said third actuable valve are open
and said second actuable valve is closed, and a second
configuration for high speed, low torque operation wherein said
second actuable valve is open and said first actuable valve and
said third actuable valve are closed; and a return port adapted to
deliver working fluid to said hydraulic pump; wherein in said first
configuration, said working fluid exits said hydraulic manifold
apparatus through said first output port and said second output
port simultaneously and returns into said hydraulic manifold
apparatus through said first intake port and said second intake
port simultaneously to permit low speed, high torque operation of
said hydraulic motor, and wherein in said second configuration,
said working fluid exits said hydraulic manifold apparatus through
said first output port, returns into said hydraulic manifold
apparatus through said first intake port, exits said hydraulic
manifold apparatus through said second output port, and returns
into said hydraulic manifold apparatus through said second intake
port to permit high speed, low torque operation of said hydraulic
motor.
2. A hydraulic manifold apparatus operable in a low speed, high
torque configuration or a high speed, low torque configuration,
said hydraulic manifold apparatus comprising: a supply port adapted
to receive pressurized working fluid from a hydraulic pump; a first
and second output port connectable to an intake of a hydraulic
motor; a first and second intake port connectable to an output of
said hydraulic motor; a first, second, and third actuable valve for
controlling the flow of said working fluid through said hydraulic
manifold apparatus; actuation means including a first solenoid for
actuating said first actuable valve and said third actuable valve
and a second solenoid for actuating said second actuable valve in
said hydraulic manifold apparatus between a first configuration for
low speed, high torque operation wherein said first actuable valve
and said third actuable valve are open and said second actuable
valve is closed, and a second configuration for high speed, low
torque operation wherein said second actuable valve is open and
said first actuable valve and said third actuable valve are closed;
and a return port adapted to deliver working fluid to said
hydraulic pump; wherein in said first configuration, said working
fluid exits said hydraulic manifold apparatus through said first
output port and said second output port simultaneously and returns
into said hydraulic manifold apparatus through said first intake
port and said second intake port simultaneously to permit low
speed, high torque operation of said hydraulic motor, and wherein
in said second configuration, said working fluid exits said
hydraulic manifold apparatus through said first output port,
returns into said hydraulic manifold apparatus through said first
intake port, exits said hydraulic manifold apparatus through said
second output port, and returns into said hydraulic manifold
apparatus through said second intake port to permit high speed, low
torque operation of said hydraulic motor.
3. A hydraulic control system for controlling a topdrive motor in a
drilling operation, comprising: a supply means for receiving
pressurized working fluid from a pump; a first and second output
means for connection to an intake of a hydraulic motor; a first and
second intake means constructed and arranged for connection to an
output of said hydraulic motor; a first, second, and third valve
means, wherein said first valve means comprises a first valve
coupled to electrically activated solenoid means; said second valve
means comprises a second valve coupled to said electrically
activated solenoid means; and said third valve means comprises a
third valve coupled to said electrically activated solenoid means;
actuation means including electrical actuator means with a first
electrical actuator for actuating said first valve and said third
valve; and a second electrical actuator for actuating said second
valve, the electrical actuator means for actuating said solenoid
means so as to control said first, second, and third valve means
between selecting an open and closed position and thus to control
said hydraulic control system between a first, low speed, high
torque configuration wherein said electrical actuator means is
actuated so as to open said first valve and said third valve and
close said second valve, and a second, high speed, low torque
configuration wherein said electrical actuator means is actuated so
as to cause opening of said second valve and closing of said first
valve and said third valve; a return means adapted to return
working fluid to said pump; wherein in said first configuration,
said working fluid exits said hydraulic control system through said
first output means and said second output means simultaneously and
returns into said hydraulic control system through said first
intake means and said second intake means simultaneously to permit
low speed, high torque operation of said hydraulic motor, and in
said second configuration, said working fluid exits said hydraulic
control system through said first output means, returns into said
hydraulic control system through said first intake means, exits
said hydraulic control system through said second output means, and
returns into said hydraulic control system through said second
intake means to permit high speed, low torque operation of said
hydraulic motor.
4. The hydraulic control system according to claim 3, wherein said
actuation means comprises: a first solenoid coupled to said first
valve; a second solenoid coupled to said second valve; and a third
solenoid coupled to said third valve.
5. The hydraulic control system according to claim 3, wherein said
electrical actuator means further comprises: a first electrical
actuator for actuating said electrically activated solenoid means
of said first valve; a second electrical actuator for actuating
said electrically activated solenoid means of said second valve;
and a third electrical actuator for actuating said electrically
activated solenoid means of said third valve.
6. A hydraulic manifold operable in a low speed, high torque
configuration or high speed, low torque configuration, said
hydraulic manifold comprising: a supply port adapted to receive
pressurized working fluid from a pump; a first and second output
port connectable to an intake of a hydraulic motor; a first and
second intake port connectable to an output of said hydraulic
motor; a first, second, and third actuable valve for controlling
the flow of said working fluid through said hydraulic manifold; a
first, second, and third electrical actuator for actuating said
first actuable valve, said second actuable valve, and said third
actuable valve, respectively, and a return port adapted to deliver
working fluid to said pump; wherein in said low speed, high torque
configuration, said second actuable valve is closed and said first
electrical actuator and said third electrical actuator actuate said
first actuable valve and said third actuable valve, respectively,
to open said first valve and said third valve and in said high
speed, low torque configuration, said first actuable valve and said
third actuable valve are closed and said second electrical actuator
actuates said second actuable valve to open said second actuable
valve.
7. A hydraulic control system for controlling a topdrive motor in a
drilling operation, comprising: a supply means for receiving
pressurized working fluid from a pump; a first and second output
means for connection to an intake of a hydraulic motor; a first and
second intake means constructed and arranged for connection to an
output of said hydraulic motor; a first, second, and third valve
means, wherein said first valve means comprises a first valve
coupled to electrically activated solenoid means; said second valve
means comprises a second valve coupled to said electrically
activated solenoid means; and said third valve means comprises a
third valve coupled to said electrically activated solenoid means;
actuation means including electrical actuator means with a first
electrical actuator for actuating said first valve; and a second
electrical actuator for actuating said second valve and said third
valve, the electrical actuator for actuating said solenoid means so
as to control said first, second, and third valve means between
selecting an open and closed position and thus to control said
hydraulic control system between a first, low speed, high torque
configuration wherein said electrical actuator means is actuated so
as to open said first valve and said third valve and close said
second valve, and a second, high speed, low torque configuration
wherein said electrical actuator means is actuated so as to cause
opening of said second valve and closing of said first valve and
said third valve; a return means adapted to return working fluid to
said pump; wherein in said first configuration, said working fluid
exits said hydraulic control system through said first output means
and said second output means simultaneously and returns into said
hydraulic control system through said first intake means and said
second intake means simultaneously to permit low speed, high torque
operation of said hydraulic motor, and in said second
configuration, said working fluid exits said hydraulic control
system through said first output means, returns into said hydraulic
control system through said first intake means, exits said
hydraulic control system through said second output means, and
returns into said hydraulic control system through said second
intake means to permit high speed, low torque operation of said
hydraulic motor.
8. The hydraulic control system according to claim 7, wherein said
actuation means comprises: a first solenoid coupled to said first
valve; a second solenoid coupled to said second valve; and a third
solenoid coupled to said third valve.
9. The hydraulic control system according to claim 7, wherein said
electrical actuator means comprises: a third electrical actuator
for actuating said electrically activated solenoid means of said
third valve.
10. A hydraulic control system for controlling a topdrive motor in
a drilling operation, comprising: a supply means for receiving
pressurized working fluid from a pump; a first and second output
means for connection to an intake of a hydraulic motor; a first and
second intake means constructed and arranged for connection to an
output of said hydraulic motor; a first, second, and third valve
means; actuation means for configuring said hydraulic control
system between a first configuration wherein said first valve means
and said third valve means are open while said second valve means
is closed and a second configuration wherein said second valve
means is open and said first valve means and said third valve means
is closed, the actuation means including a first solenoid coupled
to said first valve means; a second solenoid coupled to said second
valve means; and a third solenoid coupled to said third valve
means; a return means adapted to return working fluid to said pump;
wherein in said first configuration, said working fluid exits said
hydraulic control system through said first output means and said
second output means simultaneously and returns into said hydraulic
control system through said first intake means and said second
intake means simultaneously to permit low speed, high torque
operation of said hydraulic motor, and in said second
configuration, said working fluid exits said hydraulic control
system through said first output means, returns into said hydraulic
control system through said first intake means, exits said
hydraulic control system through said second output means, and
returns into said hydraulic control system through said second
intake means to permit high speed, low torque operation of said
hydraulic motor.
11. The hydraulic control system according to claim 10, wherein
said first valve means comprises a first valve and the first
solenoid is electrically activated; said second valve means
comprises a second valve and the second solenoid is electrically
activated; and said third valve means comprises a third valve and
the third solenoid is electrically activated.
12. The hydraulic control system according to claim 11, wherein the
first configuration is a low speed, high torque configuration, and
the second configuration is a high speed, low torque
configuration.
13. The hydraulic control system according to claim 12, wherein
said actuation means comprises: a first electrical actuator for
actuating said first valve and said third valve; and a second
electrical actuator for actuating said second valve.
14. The hydraulic control system according to claim 12, wherein
said electrical actuator means comprises: a first electrical
actuator for actuating said first valve; and a second electrical
actuator for actuating said second valve and said third valve.
15. The hydraulic control system according to claim 10, wherein
said electrical actuator means comprises: a first electrical
actuator for actuating said first solenoid; a second electrical
actuator for actuating said second solenoid; and a third electrical
actuator for actuating said third solenoid.
16. The hydraulic control system according to claim 10, wherein
said actuation means comprises an electrical actuator for actuating
said first valve means, said second valve means, and said third
valve means.
17. A hydraulic control system for controlling a topdrive motor in
a drilling operation, comprising: a supply means for receiving
pressurized working fluid from a pump; a first and second output
means for connection to an intake of a hydraulic motor; a first and
second intake means constructed and arranged for connection to an
output of said hydraulic motor; a first, second, and third valve
means; actuation means for configuring said hydraulic control
system between a first configuration wherein said first valve means
and said third valve means are open while said second valve means
is closed and a second configuration wherein said second valve
means is open and said first valve means and said third valve means
are closed, the actuation means comprising a first electrical
actuator for actuating an electrically actuated solenoid means of
the first valve means; a second electrical actuator for actuating
an electrically actuated solenoid means of the second valve means;
and a third electrical actuator for actuating an electrically
actuated solenoid means of the third valve means; a return means
adapted to return working fluid to said pump; wherein in said first
configuration, said working fluid exits said hydraulic control
system through said first output means and said second output means
simultaneously and returns into said hydraulic control system
through said first intake means and said second intake means
simultaneously to permit low speed, high torque operation of said
hydraulic motor, and in said second configuration, said working
fluid exits said hydraulic control system through said first output
means, returns into said hydraulic control system through said
first intake means, exits said hydraulic control system through
said second output means, and returns into said hydraulic control
system through said second intake means to permit high speed, low
torque operation of said hydraulic motor.
18. The hydraulic control system according to claim 17, wherein
said first valve means comprises a first valve; said second valve
means comprises a second valve; and said third valve means
comprises a third valve.
19. The hydraulic control system according to claim 18, wherein the
first configuration is a low speed, high torque configuration, and
the second configuration is a high speed, low torque
configuration.
20. The hydraulic control system according to claim 17, wherein the
actuation means including a first solenoid coupled to said first
valve means; a second solenoid coupled to said second valve means;
and a third solenoid coupled to said third valve means.
Description
FIELD OF THE INVENTION
The prevent invention relates to control equipment for powering
hydraulic motors used in oil well drilling, and more particularly
to a dual configuration hydraulic manifold operatively connected to
a dual stage motor for use in the topdrive of drilling operations.
The hydraulic manifold is switchable from a low speed, high torque
configuration to a high speed, low torque configuration.
BACKGROUND
Downhole drilling requires a mechanism for rotating a drillstring.
Traditionally, this rotation was created by a rotary table.
However, rotary tables have largely been replaced by topdrives,
which have the advantage of permitting the drilling to be done with
three joint strands rather than a one joint strand.
Hydraulically-powered motors are typically used (although electric
motors may instead be used) to rotate the topdrive and thereby
impart rotation to the drillstring. Typically, in the case of a
hydraulic motor, a pump pressurizes and circulates working fluid
through a manifold, which controls fluid flow into the motor of the
topdrive.
In two-speed prior art control systems for hydraulic motors using a
four-port motor having two fluid intakes and two fluid outputs, the
hydraulic fluid may be simultaneously be pumped into the motor's
two intakes and out through the motor's two outputs. This
arrangement is used when low speed, high torque is required from
the motor, for example when the drill is moving through high
density substances. Alternatively, when the drill is moving through
low density substances, the motor is run at high speed, low torque.
However, during high speed, low torque operation, the manifold is
typically arranged so that one of the manifold intakes and one of
the manifold outputs is "dead ended". This disadvantageously
results in a loss of energy due to vicious flow, creation of heat,
and friction loss.
A real need thus exists for a hydraulic motor control that is
capable of providing working fluid to a hydraulic motor that
operates at low speed, high torque or at high speed, low torque,
and that can switch between the two operating conditions without
power loss.
SUMMARY OF THE INVENTION
The invention provides an improved hydraulic manifold for use in
the topdrive of a drilling operation, the manifold having two
alternatively-selectable configurations, which provide working
fluid to a motor operating in either a low speed, high torque
configuration or a high speed, low torque configuration.
Accordingly, in one broad aspect of the present invention, the
invention comprises a hydraulic manifold apparatus operable in a
low speed, high torque configuration or a high speed, low torque
configuration, said hydraulic manifold apparatus comprising:
a supply port adapted to receive pressurized working fluid from a
hydraulic pump;
a first and second output port connectable to an intake of a
hydraulic motor;
a first and second intake port connectable to an output of said
hydraulic motor;
a first, second, and third actuable valve for controlling the flow
of said working fluid through said hydraulic manifold
apparatus;
actuation means for controlling said first, second, and third
valves in said hydraulic manifold apparatus between a first
configuration for low speed, high torque operation wherein said
first actuable valve and said third actuable valve are open and
said second actuable valve is closed, and a second configuration
for high speed, low torque operation wherein said second actuable
valve is open and said first actuable valve and said third actuable
valve are closed; and
a return port adapted to deliver working fluid to said hydraulic
pump;
wherein in said first configuration, said working fluid exits said
hydraulic manifold apparatus through said first output port and
said second output port simultaneously and returns into said
hydraulic manifold apparatus through said first intake port and
said second intake port simultaneously to permit low speed, high
torque operation of said hydraulic motor, and wherein in said
second configuration, said working fluid exits said hydraulic
manifold apparatus through said first output port, returns into
said hydraulic manifold apparatus through said first intake port,
exits said hydraulic manifold apparatus through said second output
port, and returns into said hydraulic manifold apparatus through
said second intake port to permit high speed, low torque operation
of said hydraulic motor.
In a further broad aspect of the invention, the invention comprises
a hydraulic control system for controlling a topdrive motor in a
drilling operation, comprising:
a supply means for receiving pressurized working fluid from a
pump;
a first and second output means for connection to an intake of a
hydraulic motor;
a first and second intake means constructed and arranged for
connection to an output of said hydraulic motor;
a first, second, and third valve means;
actuation means for configuring said hydraulic manifold system
between a first configuration wherein said first valve means and
said third valve means are open while said second valve means is
closed and a second configuration wherein said second valve means
is open and said first valve means and said third valve means is
closed;
a return means adapted to return working fluid to said pump;
wherein in said first configuration, said working fluid exits said
hydraulic control system through said first output means and said
second output means simultaneously and returns into said hydraulic
control system through said first intake means and said second
intake means simultaneously to permit low speed, high torque
operation of said hydraulic motor, and in said second
configuration, said working fluid exits said hydraulic control
system through said first output means, returns into said hydraulic
control system through said first intake means, exits said
hydraulic control system through said second output means, and
returns into said hydraulic control system through said second
intake means to permit high speed, low torque operation of said
hydraulic motor.
In still a further broad aspect of the invention, the invention
comprises a hydraulic manifold operable in a low speed, high torque
configuration or high speed, low torque configuration, said
hydraulic manifold comprising:
a supply port adapted to receive pressurized working fluid from a
pump;
a first and second output port connectable to an intake of a
hydraulic motor;
a first and second intake port connectable to an output of said
hydraulic motor;
a first, second, and third actuable valve for controlling the flow
of said working fluid through said hydraulic manifold;
a first, second, and third electrical actuator for actuating said
first actuable valve, said second actuable valve, and said third
actuable valve, respectively, and
a return port adapted to deliver working fluid to said pump;
wherein in said low speed, high torque configuration, said second
actuable valve is closed and said first electrical actuator and
said third electrical actuator actuate said first actuable valve
and said third actuable valve, respectively, to open said first
valve and said third valve and in said high speed, low torque
configuration, said first actuable valve and said third actuable
valve are closed and said second electrical actuator actuates said
second actuable valve to open said second actuable valve.
BRIEF DESCRIPTION OF THE FIGURES
FIG. 1 is a side view of a topdrive unit of the prior art;
comprising a control manifold and a hydraulically powered
motor;
FIG. 2 is an exploded side view of an embodiment of the hydraulic
control manifold of the present invention, showing its connection
to a hydraulic motor;
FIG. 3A is a cross section of an embodiment of a hydraulic manifold
of the invention according to FIG. 2, in a low speed, high torque
configuration;
FIG. 3B is a cross section of an embodiment of a hydraulic manifold
of the invention according to FIG. 2, in a high speed, low torque
configuration;
FIG. 4A is a schematic diagram of a first embodiment of actuation
means in a first configuration;
FIG. 4B is a schematic diagram of the actuation means of FIG. 4A in
a second configuration;
FIG. 5A is a schematic of a second embodiment of actuation means;
and
FIG. 5B is a variation of the second embodiment shown in FIG.
5A.
DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS
Referring to FIG. 1, a prior art hydraulic system 1 is shown. The
hydraulic system 1 comprises a hydraulic fluid pump (not shown) for
supplying pressurized hydraulic fluid, a hydraulic manifold 3 for
receiving said pressurized hydraulic fluid, and a motor unit 5
comprising two motors 5a, 5b that drives a topdrive unit (not
shown). The hydraulic manifold 3 receives pressurized working fluid
from the pump via supply port 2, and returns working fluid to the
pump via return port 8. The prior art hydraulic manifold 3
comprises two output ports, A1 and B1, which are operationally
connectable to two intake ports, A2 and B2, respectively on motor
unit 5. The motor unit 5 additionally comprises two output ports,
C2 and D2, which are operatively connectable to hydraulic return
port 8, which is in fluid communication with the hydraulic fluid
pump (not shown).
The prior art hydraulic system 1 of FIG. 1 may be operated in a low
speed, high torque configuration. In this configuration, working
fluid exits the hydraulic manifold 3 through output ports A1 and E1
on the manifold 3 and enters the motor 5 through the intake ports
A2 and B2, respectively, on motor 5. Once the working fluid has
circulated through the motor 5, it exits through output ports C2 an
D2 on motor 5 and is returned to the pump via return 8.
The prior art hydraulic system 1 may also be operated in a high
speed, low torque configuration. In this configuration hydraulic
fluid flow out of one of the output ports A1 on the manifold 3 is
"dead ended" so that working fluid is pumped through hydraulic
manifold 3 through only one output B1 to motor unit 5.
Correspondingly, once the working fluid has circulated through the
motor 5, it exits the motor 5 through only one output. Accordingly,
fluid continues to circulate within the entire motor unit 5, and in
particular both of motors 5a, 5b even though only one motor 5a or
5b is receiving pressurized hydraulic fluid from manifold 3. This
disadvantageously results in a loss of energy due to viscous flow,
the creation of heat, and friction loss.
In other prior art hydraulic systems (not shown), working fluid
that has circulated through a motor is returned to the manifold
through two different intake ports on the manifold. When said
system is operating at high speed, low torque, one of the intake
ports on the manifold is similarly "dead ended" so that the working
fluid is returned to the manifold through only one port. This again
likewise disadvantageously results in a loss of energy due to
viscous flow, the creation of heat, and friction loss within the
motor of a two motor system which is not receiving pressurized
hydraulic fluid and is effectively "dead ended".
Referring to FIG. 2, FIG. 2 shows an embodiment of an inventive
dual configuration hydraulic manifold system 10 of the present
invention. The hydraulic system 10 comprises a pump (not shown), a
hydraulic manifold 30, and a motor unit 50, comprising two motors
50a, 50b, stacked one on top of the other and coupled together on a
common shaft (not shown). The hydraulic manifold 30 receives
pressurized working fluid from the pump via connector 32 and intake
means 34. The pressure of the fluid will depend on the torque
requirements of motor unit 50, and may be as high as 5,000 psi.
After circulating through the motor 50 and returning to the
hydraulic manifold 30 (as described below), working fluid is
returned to the pump through output 36 and connector 38.
The hydraulic manifold 30 comprises four ports for mating with the
motor unit 50, two output ports A1 and C1 and two intake ports B1
and D1. Ports A1, C1, and D1 are preferably arranged linearly in a
vertical plane with port B1 positioned adjacent to port C1.
Motor unit 50 is preferably a dual stage motor, i.e. containing two
motors 50a, 50b on one shaft in a single casing. A motor unit 50 of
this type, for example is a four port, 125 series double stack
motor, code 62, supplied from Rineer Hydraulics, Inc..RTM.. The
motor 50 comprises four ports for mating with manifold 30, two
intake ports A2 and C2, in operational connection with hydraulic
manifold 30 output ports A1 and C1, respectively, and two output
ports B2 and D2, in operational connection with hydraulic manifold
30 intake ports B1 and D1. Ports A2, C2, and D2 are preferably
arranged linearly in a vertical plane with port B2 positioned
adjacent to port C2.
The hydraulic manifold 30 further comprises three internal valves
31, 33, 35 (not visible in FIG. 2, but described further below and
shown in FIGS. 3A, 3B, 4A, 4B, 5A, and 5B) which permit the
hydraulic manifold 30 to switch between a low speed, high torque
configuration and a high speed, low torque configuration, and
without having to replace or exchange the hydraulic manifold 30 or
motor unit 50. Preferably, valves 31, 33, 35 comprise ball valves,
but may contain any other type of valves known to a person of skill
in the art, including a solenoid actuated ball valve, gate valve,
butterfly valve or the like. For example, valves 31, 33, 35 may
each comprise solenoid actuated ball valves, comprising 24-volt
solenoids operating such ball valves and contained in an explosion
proof container.
Referring to FIG. 3A, the hydraulic manifold 30 is shown operating
in a low speed, high torque configuration. As described above, the
hydraulic manifold 30 contains valves 31, 33, and 35, which control
the flow of working fluid through hydraulic manifold 30 and thereby
into motor unit 50. Valves 31, 33, and 35 are preferably aligned
linearly in a vertical fashion within manifold 30, as shown in
FIGS. 3A and 3B.
In the low speed, high torque configuration, with reference to FIG.
2 and FIG. 3A, valves 31 and 35 are actuated to be open while valve
33 is actuated to be closed. Working fluid from the pump enters
manifold 30 through connector 32 and intake 34 (shown in bolded
arrows). With valve 33 closed, pressurized hydraulic fluid flows
through manifold 30 and through both output ports A1 and C1 and
into corresponding intake ports A2 and C2, respectively, on motor
unit 50. Working fluid therefore enters both motor 50a via output
port A2 and motor 50b via output port B2 and thus in parallel.
After circulating through motors 50a, 50b the fluid flows (shown in
stippled arrows) through output ports B2 and D2 on motors 50a, 50b
respectively and into intake ports B1 and D1, respectively of
manifold 30. With valve 35 open and valve 33 closed, the working
fluid returned from the motor unit 50 moves through the manifold 30
and through output 36 into connector 38 to be returned to the
pump.
Referring to FIGS. 2 and 3B, the hydraulic manifold 30 is shown
operating motor unit 50 in a high speed, low torque configuration.
In this configuration, valve 33 is open and valves 31 and 35 are
closed. Working fluid from the pump enters manifold 30 through
connector 32 and intake 34 (shown in bolded arrows). With valve 31
actuated to the closed position, the working fluid flows through
manifold 30 and through output port A1 and into corresponding
intake port A2 on motor 50a. After circulating through a first
motor 50a, the fluid flows through output port B2 on motor unit 50
and into intake port B1 of manifold 30. With valve 33 actuated open
and valve 35 actuated closed, the working fluid (shown in dashed
arrows) then flows through output port C1 and into corresponding
intake port C2 on motor 50b. After circulating through motor 50b,
the fluid flows through output D2 on motor 50b and into intake port
D1 on manifold 30 (shown in dotted arrows). With valve 35 actuated
closed, the fluid returned from the motor 50b moves through the
manifold 30 and through output 36 into connector 38 to be returned
to the pump. Therefore, during high speed, low torque operation,
working fluid passes through both motors 50a, 50b of motor unit 50
in series.
Referring to FIG. 4A, actuation means 40 is shown for opening and
closing valves 31, 33, and 35 to allow hydraulic manifold 30 to
switch between a low speed, high torque configuration and a high
speed, low torque configuration. Preferably, actuation means 40
comprises electrical actuation means. Actuation means 40 is
operationally connected to device 42 through which bar 52 passes.
Bar 52 is in mechanical communication with valves 31, 33, and 35
through linkages 32, 34, and 36, respectively. The balls of valves
31 and 35 are positioned in the same orientation while the ball of
valve 35 is oriented 90 degrees thereto. In the low speed, high
torque configuration, valves 31 and 35 are open and valve 33 is
closed. When the high speed, low torque configuration is desired,
actuation means 40 is activated to cause bar 52 to move a
predetermined distance through device 42. The movement of bar 52
causes linkages 32, 34, and 36 to rotate and thereby cause valves
31, 33, and 35 to rotate so that valve 33 opens and valves 31 and
35 close (as shown in FIG. 4B). When the low speed, high torque
configuration is desired again, actuation means 40 is deactivated
and bar 52 returns to its original position. The return movement of
bar 52 causes linkages 32, 34, and 36 to rotate and thereby causes
valves 31, 33, and 35 to rotate so that valves 31 and 35 are opened
and valve 33 is closed.
Referring to FIG. 5A, actuation means 40 is shown for opening and
closing valves 31, 33, and 35 to allow hydraulic manifold 30 to
switch between a low speed, high torque configuration and a high
speed, low torque configuration. Preferably, actuation means 40
comprises electrical actuation means. In this embodiment, each of
valves 31, 33, and 35 is coupled to an electrically activated
solenoid means. Preferably, the electrically activated solenoid
means comprise solenoid 61 coupled to valve 31, solenoid 63 coupled
to valve 33, and solenoid 65 coupled to valve 35. Each solenoid 61,
63, and 65 receives a separate input from actuation means 40.
Solenoid 61 is connected to actuation means 40 via lead 51,
solenoid 63 is connected to actuation means 40 via lead 53, and
solenoid 65 is connected to actuation means 40 via lead 55. In the
low speed, high torque configuration, actuation means 40 actuates
solenoids 61 and 65, through leads 51 and 55, to open valves 31 and
35. When the high speed, low torque configuration is desired,
actuator means 40 is activated to actuate solenoid 63, through lead
53, to open valve 33, and discontinues actuating solenoids 61 and
65, causing valves 31 and 35 to close.
Referring to FIG. 5B, a variation of the leads connecting actuation
means 40 to solenoids 61, 63, and 65 is shown. In this embodiment,
solenoid 63 is connected to actuation means 40 via lead 53 and
solenoids 61 and 65 are connected through common lead 57. In the
low speed, high torque configuration, actuation means 40 actuates
solenoids 61 and 65, through common lead 57, to open valves 31 and
35. When the high speed, low torque configuration is desired,
actuator means 40 actuate solenoid 63, through lead 53, to open
valve 33, and discontinues actuating solenoids 61 and 65, causing
valves 31 and 35 to close.
The foregoing description of the disclosed embodiments is provided
to enable any person skilled in the art to make or use the present
invention. The scope of the claims should not be limited by the
preferred embodiments set forth in the examples, but should be
given the broadest interpretation consistent with the description
as a whole. Thus, the present invention is not intended to be
limited to the embodiments shown herein, but is to be accorded the
full scope consistent with the claims, wherein reference to an
element in the singular, such as by use of the article "a" or "an"
is not intended to mean "one and only one" unless specifically so
stated, but rather "one or more". In addition, where reference to
"fluid" is made, such term is considered meaning all liquids and
gases having fluid properties.
For a complete definition of the invention and its intended scope,
reference is to be made to the summary of the invention and the
appended claims read together with and considered with the
disclosure and drawings herein.
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